CA1200148A - Double axle drive for rail traction vehicles - Google Patents
Double axle drive for rail traction vehiclesInfo
- Publication number
- CA1200148A CA1200148A CA000415042A CA415042A CA1200148A CA 1200148 A CA1200148 A CA 1200148A CA 000415042 A CA000415042 A CA 000415042A CA 415042 A CA415042 A CA 415042A CA 1200148 A CA1200148 A CA 1200148A
- Authority
- CA
- Canada
- Prior art keywords
- coupling
- drive
- halves
- axles
- ring
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B61—RAILWAYS
- B61C—LOCOMOTIVES; MOTOR RAILCARS
- B61C9/00—Locomotives or motor railcars characterised by the type of transmission system used; Transmission systems specially adapted for locomotives or motor railcars
- B61C9/38—Transmission systems in or for locomotives or motor railcars with electric motor propulsion
- B61C9/52—Transmission systems in or for locomotives or motor railcars with electric motor propulsion with transmission shafts at an angle to the driving axles
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
- F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
- F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
- F16D3/226—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a cylinder co-axial with the respective coupling part
- F16D3/227—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a cylinder co-axial with the respective coupling part the joints being telescopic
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
- F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
- F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
- F16D2003/22326—Attachments to the outer joint member, i.e. attachments to the exterior of the outer joint member or to the shaft of the outer joint member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2300/00—Special features for couplings or clutches
- F16D2300/22—Vibration damping
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Vehicle Body Suspensions (AREA)
- Motor Power Transmission Devices (AREA)
- Vibration Prevention Devices (AREA)
- Retarders (AREA)
- Vehicle Cleaning, Maintenance, Repair, Refitting, And Outriggers (AREA)
- Automatic Cycles, And Cycles In General (AREA)
- Press Drives And Press Lines (AREA)
- Polysaccharides And Polysaccharide Derivatives (AREA)
- Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)
- Train Traffic Observation, Control, And Security (AREA)
- Electric Propulsion And Braking For Vehicles (AREA)
- Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)
Abstract
ABSTRACT
A double axle drive for rail traction vehicles including a bogie frame between the axles and a drive motor thereon with the drive shaft extending at right angles to the rail axles and the rail axles driven by angular gears and couplings between the motor and gear drives for the axles where the couplings are in halves interconnected by a torsionally flexible juncture between the halves which is unstressed except in torsion and flexural misalignment of the shafts and the driving and driven shafts are connected to the coupling by ball and socket joints having balls in axially extending pockets so that no axial stresses are induced into the coupling. In one form, the coupling includes radial and axial facing bushings for a centering sliding relationship and in another form, a direct annular plate connection exists between the couplings and in still another form, pins extend axially through a rubber torsionally elastic joint.
A double axle drive for rail traction vehicles including a bogie frame between the axles and a drive motor thereon with the drive shaft extending at right angles to the rail axles and the rail axles driven by angular gears and couplings between the motor and gear drives for the axles where the couplings are in halves interconnected by a torsionally flexible juncture between the halves which is unstressed except in torsion and flexural misalignment of the shafts and the driving and driven shafts are connected to the coupling by ball and socket joints having balls in axially extending pockets so that no axial stresses are induced into the coupling. In one form, the coupling includes radial and axial facing bushings for a centering sliding relationship and in another form, a direct annular plate connection exists between the couplings and in still another form, pins extend axially through a rubber torsionally elastic joint.
Description
~2~
SP~CIFICATION
The invention relates to improvements in double axle drive for rail traction vehicles which include a drive motor mounted in the bogie frame between the axles w1th the drive motor having its ~ower output shafts extend:lng in the direction of travel of the vehicle~ and particularl~ relates to improvements in the construction for coupling the drive motor to the rail axles.
In rail drives having double axles on a bogie frame, the rotational drive power to the axles is derived by angular gear drives with a pinion driving a larger gear on the axle. Torque is transmitted to the pinion from the motor by a coupling.
A double axle drive of the type above described is shown in German OS 26 0l 516 wherein two rubber block couplings are disposed between the drive motor and angular drive gears. This construction provides for angular mobility and torsional elasticity, bu~ disadvantaqes are present in that the prestress o~ the individual rubber blocks of the coupling is very high because of the simultaneous action of tor~ue and centrifugal force. This makes assembly very difficult. Despite the high prestress, an increasing speed produces an increasing unbalanced force which, because of the uneven settling process of the rubber is not definable and provides a factor of considerable uncertainty in design and operation~
It is accordingly an object of the invention to provide an improved ~oupling which exhibits high anqular mobility, is assembled without prestress, and which operates faultlessly centered over all speed ran~es even the speed ranges necessary for rotary current drive te~-,nology.
It is a further object of the invention to provide an improved combination drive utilizing a coupling which has ruggedness and useful long life required for rail traction vehicles and is capable o~ being equipped with spring elements which are torsionally elastic.
A feature of the invention is the provision of a flexible coupling which eliminates prestressed joints and which allows for axial expansion and contraction and adjustment by providing ball and socket joints having at least one restrictive row of balls in two coupling halves.
The ball and socket ~oints which accommodate axial shifting between the coupling and the driven shaft and the driving shaft can be assembled without a restoring force. The two shaft ends run faultlessly centered and no unbalance results even at high speeds.
It is another feature of the invention to provide a torsionally elastic centering element which is disposed between the coupling halves. As a result of a torsionally elastic centering element, it is possible to design the coupling in such a manner that it not only allows high excursion movement and forces and can be assembled and reassembled without a restoring force, but ;s also torsionally elastic and operates torsionally elastic without precise centering being lost. By this arranqement, a
SP~CIFICATION
The invention relates to improvements in double axle drive for rail traction vehicles which include a drive motor mounted in the bogie frame between the axles w1th the drive motor having its ~ower output shafts extend:lng in the direction of travel of the vehicle~ and particularl~ relates to improvements in the construction for coupling the drive motor to the rail axles.
In rail drives having double axles on a bogie frame, the rotational drive power to the axles is derived by angular gear drives with a pinion driving a larger gear on the axle. Torque is transmitted to the pinion from the motor by a coupling.
A double axle drive of the type above described is shown in German OS 26 0l 516 wherein two rubber block couplings are disposed between the drive motor and angular drive gears. This construction provides for angular mobility and torsional elasticity, bu~ disadvantaqes are present in that the prestress o~ the individual rubber blocks of the coupling is very high because of the simultaneous action of tor~ue and centrifugal force. This makes assembly very difficult. Despite the high prestress, an increasing speed produces an increasing unbalanced force which, because of the uneven settling process of the rubber is not definable and provides a factor of considerable uncertainty in design and operation~
It is accordingly an object of the invention to provide an improved ~oupling which exhibits high anqular mobility, is assembled without prestress, and which operates faultlessly centered over all speed ran~es even the speed ranges necessary for rotary current drive te~-,nology.
It is a further object of the invention to provide an improved combination drive utilizing a coupling which has ruggedness and useful long life required for rail traction vehicles and is capable o~ being equipped with spring elements which are torsionally elastic.
A feature of the invention is the provision of a flexible coupling which eliminates prestressed joints and which allows for axial expansion and contraction and adjustment by providing ball and socket joints having at least one restrictive row of balls in two coupling halves.
The ball and socket ~oints which accommodate axial shifting between the coupling and the driven shaft and the driving shaft can be assembled without a restoring force. The two shaft ends run faultlessly centered and no unbalance results even at high speeds.
It is another feature of the invention to provide a torsionally elastic centering element which is disposed between the coupling halves. As a result of a torsionally elastic centering element, it is possible to design the coupling in such a manner that it not only allows high excursion movement and forces and can be assembled and reassembled without a restoring force, but ;s also torsionally elastic and operates torsionally elastic without precise centering being lost. By this arranqement, a
2~ coupling is achieved which not only utilizes oppvsed coupling sections or halves which are centered, but which are torsionally elastic.
In accordance with the invention, an elastic centering element utilizes a centering ring on one side and a centering pin on the other side~ A normal centering on one side of the corpling is obtained as a result of the 2~
centering ring and a free outside space for a torsionally elastic torque transmitting element is available at the other coupling side as a result of the centering pin~
A further feature of the coupling construction is that the centering element includes sliding elements at the side of the centering pin. As a result of these sli~ing elements, the coupling halves can move relative to each other without developing friction and without rust occurring. Nevertheless, a precise axial and radial guidance is attained. Therefore, radially and axially effective guide elements are obtained in the form of a sliding sleeve or floating bushing and a double sliding disk which serve as the sliding members. Thus, the coupling derives the advantages which are equal to threade~ or screwed flange parts with respect to the centerinq of the running or axial alignment but which also allows movement of the individual coupling halves relative to each other.
It is a further feature of the invention ~hat at least one elastic ring, preferably of rubber is provided for transmitting the torque and is disposed in the centering element in the area of the centering pin~ The desired torsional elasticity achieved by means of the elastic ring which is pref rably oE rubber in order to exploit the self-dampening properties of rubber. A ring disposed around the centering pin advantageously can be connected without prestress to the centering element relative to disadvantages of screw type connections and outer rings. Thust the desired ease of assembl~ and disassembly has also been made possible. Further, no imbalances derive even at high speeds inasmuch as an outer ring of metal ~urrounds the elastic ring and provides a reliable fixing of the elastic rinq in ~2~
the centering element.
~ further feature of the invention is that the coupling at the side of the centering pin is designed in dual parts so that an axially effective member is dispo~ed between the parts. The axial position of all parts of the coupling relative to one another is securely fixed in as complete a manner as is the radial position which is determined by a sliding sleeve or floating bushin~ and centering ring and outer ring. The arrangement allows a certain rotational mobility of the cou~ling halves relative to each other, ana provides overall centering which is fully as effective as an intermediate centerin~ ring threaded to two coupling halves~
A further feature of the invention in another form is the provision of a three-part coupling having rubber spring elements which are profiled or shaped and are assembled without prestress. As a result of torque transmission by means of rubber spring elements mounted without prestress, a coupling which reacts softly is obtained, particularly when the rubber spring elements are profiled in the power delivery or expansion or flexure direction. The rubber spring elements are advantageously disposed in bores by means of freely movable intermediate disk parts and alternately interact with pins of one coupling side which extend through the rubber spring elements. A particularly elastic coupling is therefore derived which comprises a few simple compvnent parts and is particularly suitable for lower torques and speeds.
Other objects, advantages and features of the invention will become more apparent with khe teaching of the principles thereof in the specification9 olaims and drawings . . ,~
in which:
Figure l is an elevational shown somewhat schematically of an overall drive arrangement for a rail vehicle;
Figure 2 is a vertical sectional view taken through the axis oE a drive couPling between the drive motor and the driven rail axle Figure 3 is another sectional taken along the axis of the coupling of another form embodying the principles of the present invention and Figure 4 is a vertical sectional view taken thr~ugh a coupling embodying embodying features of the present invention.
Figure l illustrates the basic components of a double axle drive or a rail traction vehicle wherein the various elements are directly labelle~. The elastically seated motor is centrally disposed in the bogie frame between the two pairs of wheels which are mounted on cross a~les and have angular gears on the axles for driving the wheels. The drive from the motor is transmitted through driving and driven shafts joined to each other through a coupling with the shafts rotating on an axis extending in the direction of travel of the rail vehicle, that is, at right angles to the wheel a~les.
Figure 2 illustrates the internal details of a cvupling embodying the features o the invention, The coupling joins one shaft 1 to the other shaf~ la, and for purposes o description, the shaft l may be taken as the driving shaft and la as t.he driven shaft, althou~h the direction of power transmission may be in the opposite direction.
_5_ ,~
Mounted on the driving shaft 1 is a ball and socket joint hub 2 which is suitably secured such as by splines la to the shaft 1. An outer part 5 of the ball and socket joint is connected to the hub by spherical balls ~
which are arranged in circumferentially spaced pockets 2a on the hub and 5a on the outer sleeve 5. These pockets extend axially and are of uniform size being spherical in shaPe so as to seat the balls, and permit relative axial movement of the shaft. The balls are held in place by a cage 3 which has openings for the balls and which i5 held in place by an arcuate sur~ace 2b at the sides of the pocket 2a on the hub. For transmission of rotational torque from the ball and socket joint, the ring 5 of the joint is bolted by means of bolt~ ~b to a centering element 12. The centering element has a centering disk 11 integral therewith, and the centering eIement has a center pin 12a. Surrounding the centering pin 12a is a sliding or floating bushing 14.
Surrounding the bushing is a floating disk 15 which has a hub 15a surrounding the bushing 14 and an outer flange portion 15b resting against a flat axial ring 16. Two rings 16 are provided which are on opposite sides of an inwardly extending flange 12b of the member 12.
An ou~wardly extending flange 13a of the member 12 has a ring bolted thereto by throu~h-bolts such as 13b to hold a rubber torque transmitting ring R. The torque transmitting ring R may be in different forms~ and as shown in the lower part of Figure 2, R is in the form of an axially flat annular ring held in its curved conformation by the retainer ring 13. In the upper portion of Figure 2, the ring R' is held by a retainer ring 137 with through-bolts 13b' which bolt the ring to the flange 13a'~ Small movable .~_ ~2~
axial pins 13c may extend through the ring R' to aid in holding it in place, but these do not retard the rotational torque flexibility of the ring ~'.
The torque transrnittin~ rubber ring R kran mit8 rotational force to the other half of the ball and socket joint which includes an outer ring 6 with axially extending pockets 6a. Seated in the pockets are balls 7 which also seat in axially extending pockets 8a of a hub 8 w~ich is splined to the shaft la. The pockets extend axially similar to the ball and socket joint on the shaft l, and the balls are held in place by an annular cage which is axially retained on the arcuate surface 8b at the side of the pockets on the hub 8.
The torsional ring R may be spheroidally shaped in cross section, can be retangular as shown by the ring R' or can exhibit a round cross sectionO
Spacing between the shaft end la and the outer ring 6 is shown by the circled line lOo A similar spacing is provided between the shaft l and the coupling member 12. Misalignment or pivot motion of the shafts l and la occurs about the plane 18, and the axial misalignment is indicated by the arrowed dimension line shown at A.
Centering alignment and axial aliynment within the co~pling assembly are achieved through the floating bushing l~ and the floating ring 15 and by the axial disks 16 which relatively control and accommodate the position of the outer rings of the ball and socket joints and allow the torsion ring R to function to transmit driving korque and to assimilate vibrational forces. ~ssembly and disassembly of the unit is accomplished by removal of the bolts such at 5a and 13b, and the floating ring ll and part of the flat disk ~7-~2~
16 may be split or in sections to permit their assemblage.
Figure 3 illustrates another form of the coupling utilizing fewer parts and rotational mobility is reduced.
21 indicate~ the one shaft end which may, for purposes of descript;on, be designated as a drive shaft and carries a ball and socket joined hub 22 which is suitably splined to the ~haft 21. 5pherical balls 24 are seated in axially extend;ng slots in the hub 22 and held in place by an annular cage 23. An o~ter ball and socket ring 25 has axially extending slots for receiving the balls.
A centering ring 30 is disposed between the opposed ball and socket joints being located between the sleeves 25 and 26 of the joints and being held therebetween by circumferentially spaced axially extending through-bolts 30a. The rings of the ball and socket joints are centered by a shoulder 32 (shown in the encircling ring which is added to the drawing for purposes of designation). An expansion compensation ~pacing 31 is provide~ (shown by the circle to designate the area). The plane of torq~Te support or alignment accommodation is indicated at 33. The possible pivotal motion due to chan~e in alignmen~ of the shafts 21 and 29 is indicated by the arrowea lines ~9aO The driven ball and socket joint includes the outer ring 26 wi~h axially extending pockets and a hub 28 is splined to the shaft 29. Spherical balls 27 seat in the pockets of the ring 26 and in a~ially extending pockets on the hub 28, and the balls are held in place by a cage 21a.
In the arrangement of Figure 4, the coupling illu~trAted allows damping motion of the individual shafts relative to one another in ever~ directionO ~ubs 42 and 55 are mounted on and splined to respective shafts ~1 and 5~.
~ .~
~ub 42 carries a ring 43 and a ring 44 which by axiall~
extending through~bolts provides spacers to mount a drive disk 45 which preferably has a star-like design constituting an inner circular or annular portion with spaced projections. A similar construction is provided in a ring ~4 which mounts on the hub 55. To interconnect the star-like rings 45 and 54, an intermediate element is provided, and pins or bolts 47 and 51 e~tend from the star rings into the elastic rubber spring elements 49 and 53 in the center coupling member 48. Bushings 46 and 52 are provided for the pins 51 and 47. The cou~ling 53 is formed of rubber and is assembled without prestress and admits motion in all directions, but transmits rotary torque. Assimilation and vibrations and stresses is accomoodated, and yet the coupling member 53 remains in its centered position when stationary and when driving in axial alignment with the shaf~s 41 and 56. Cer~ain axial misalignment is accomModated as indicated by the arrowed lines at D~ and axial shifting of the shafts such as due to temperature change is permitted as indicated by the arrowed lines M.
Further, angular cocking of the axis of the shafts is accommodated as indicated by the arrowed dimension A.
Thus, it will be seen tha~ ~e have provided an improved coupling concept which meets the objectives and advantages above set orth and provides particular accommodation in a rail vehicle which are subject to particularly high demands concerning useful life and safety.
~9_ .,,, ~
In accordance with the invention, an elastic centering element utilizes a centering ring on one side and a centering pin on the other side~ A normal centering on one side of the corpling is obtained as a result of the 2~
centering ring and a free outside space for a torsionally elastic torque transmitting element is available at the other coupling side as a result of the centering pin~
A further feature of the coupling construction is that the centering element includes sliding elements at the side of the centering pin. As a result of these sli~ing elements, the coupling halves can move relative to each other without developing friction and without rust occurring. Nevertheless, a precise axial and radial guidance is attained. Therefore, radially and axially effective guide elements are obtained in the form of a sliding sleeve or floating bushing and a double sliding disk which serve as the sliding members. Thus, the coupling derives the advantages which are equal to threade~ or screwed flange parts with respect to the centerinq of the running or axial alignment but which also allows movement of the individual coupling halves relative to each other.
It is a further feature of the invention ~hat at least one elastic ring, preferably of rubber is provided for transmitting the torque and is disposed in the centering element in the area of the centering pin~ The desired torsional elasticity achieved by means of the elastic ring which is pref rably oE rubber in order to exploit the self-dampening properties of rubber. A ring disposed around the centering pin advantageously can be connected without prestress to the centering element relative to disadvantages of screw type connections and outer rings. Thust the desired ease of assembl~ and disassembly has also been made possible. Further, no imbalances derive even at high speeds inasmuch as an outer ring of metal ~urrounds the elastic ring and provides a reliable fixing of the elastic rinq in ~2~
the centering element.
~ further feature of the invention is that the coupling at the side of the centering pin is designed in dual parts so that an axially effective member is dispo~ed between the parts. The axial position of all parts of the coupling relative to one another is securely fixed in as complete a manner as is the radial position which is determined by a sliding sleeve or floating bushin~ and centering ring and outer ring. The arrangement allows a certain rotational mobility of the cou~ling halves relative to each other, ana provides overall centering which is fully as effective as an intermediate centerin~ ring threaded to two coupling halves~
A further feature of the invention in another form is the provision of a three-part coupling having rubber spring elements which are profiled or shaped and are assembled without prestress. As a result of torque transmission by means of rubber spring elements mounted without prestress, a coupling which reacts softly is obtained, particularly when the rubber spring elements are profiled in the power delivery or expansion or flexure direction. The rubber spring elements are advantageously disposed in bores by means of freely movable intermediate disk parts and alternately interact with pins of one coupling side which extend through the rubber spring elements. A particularly elastic coupling is therefore derived which comprises a few simple compvnent parts and is particularly suitable for lower torques and speeds.
Other objects, advantages and features of the invention will become more apparent with khe teaching of the principles thereof in the specification9 olaims and drawings . . ,~
in which:
Figure l is an elevational shown somewhat schematically of an overall drive arrangement for a rail vehicle;
Figure 2 is a vertical sectional view taken through the axis oE a drive couPling between the drive motor and the driven rail axle Figure 3 is another sectional taken along the axis of the coupling of another form embodying the principles of the present invention and Figure 4 is a vertical sectional view taken thr~ugh a coupling embodying embodying features of the present invention.
Figure l illustrates the basic components of a double axle drive or a rail traction vehicle wherein the various elements are directly labelle~. The elastically seated motor is centrally disposed in the bogie frame between the two pairs of wheels which are mounted on cross a~les and have angular gears on the axles for driving the wheels. The drive from the motor is transmitted through driving and driven shafts joined to each other through a coupling with the shafts rotating on an axis extending in the direction of travel of the rail vehicle, that is, at right angles to the wheel a~les.
Figure 2 illustrates the internal details of a cvupling embodying the features o the invention, The coupling joins one shaft 1 to the other shaf~ la, and for purposes o description, the shaft l may be taken as the driving shaft and la as t.he driven shaft, althou~h the direction of power transmission may be in the opposite direction.
_5_ ,~
Mounted on the driving shaft 1 is a ball and socket joint hub 2 which is suitably secured such as by splines la to the shaft 1. An outer part 5 of the ball and socket joint is connected to the hub by spherical balls ~
which are arranged in circumferentially spaced pockets 2a on the hub and 5a on the outer sleeve 5. These pockets extend axially and are of uniform size being spherical in shaPe so as to seat the balls, and permit relative axial movement of the shaft. The balls are held in place by a cage 3 which has openings for the balls and which i5 held in place by an arcuate sur~ace 2b at the sides of the pocket 2a on the hub. For transmission of rotational torque from the ball and socket joint, the ring 5 of the joint is bolted by means of bolt~ ~b to a centering element 12. The centering element has a centering disk 11 integral therewith, and the centering eIement has a center pin 12a. Surrounding the centering pin 12a is a sliding or floating bushing 14.
Surrounding the bushing is a floating disk 15 which has a hub 15a surrounding the bushing 14 and an outer flange portion 15b resting against a flat axial ring 16. Two rings 16 are provided which are on opposite sides of an inwardly extending flange 12b of the member 12.
An ou~wardly extending flange 13a of the member 12 has a ring bolted thereto by throu~h-bolts such as 13b to hold a rubber torque transmitting ring R. The torque transmitting ring R may be in different forms~ and as shown in the lower part of Figure 2, R is in the form of an axially flat annular ring held in its curved conformation by the retainer ring 13. In the upper portion of Figure 2, the ring R' is held by a retainer ring 137 with through-bolts 13b' which bolt the ring to the flange 13a'~ Small movable .~_ ~2~
axial pins 13c may extend through the ring R' to aid in holding it in place, but these do not retard the rotational torque flexibility of the ring ~'.
The torque transrnittin~ rubber ring R kran mit8 rotational force to the other half of the ball and socket joint which includes an outer ring 6 with axially extending pockets 6a. Seated in the pockets are balls 7 which also seat in axially extending pockets 8a of a hub 8 w~ich is splined to the shaft la. The pockets extend axially similar to the ball and socket joint on the shaft l, and the balls are held in place by an annular cage which is axially retained on the arcuate surface 8b at the side of the pockets on the hub 8.
The torsional ring R may be spheroidally shaped in cross section, can be retangular as shown by the ring R' or can exhibit a round cross sectionO
Spacing between the shaft end la and the outer ring 6 is shown by the circled line lOo A similar spacing is provided between the shaft l and the coupling member 12. Misalignment or pivot motion of the shafts l and la occurs about the plane 18, and the axial misalignment is indicated by the arrowed dimension line shown at A.
Centering alignment and axial aliynment within the co~pling assembly are achieved through the floating bushing l~ and the floating ring 15 and by the axial disks 16 which relatively control and accommodate the position of the outer rings of the ball and socket joints and allow the torsion ring R to function to transmit driving korque and to assimilate vibrational forces. ~ssembly and disassembly of the unit is accomplished by removal of the bolts such at 5a and 13b, and the floating ring ll and part of the flat disk ~7-~2~
16 may be split or in sections to permit their assemblage.
Figure 3 illustrates another form of the coupling utilizing fewer parts and rotational mobility is reduced.
21 indicate~ the one shaft end which may, for purposes of descript;on, be designated as a drive shaft and carries a ball and socket joined hub 22 which is suitably splined to the ~haft 21. 5pherical balls 24 are seated in axially extend;ng slots in the hub 22 and held in place by an annular cage 23. An o~ter ball and socket ring 25 has axially extending slots for receiving the balls.
A centering ring 30 is disposed between the opposed ball and socket joints being located between the sleeves 25 and 26 of the joints and being held therebetween by circumferentially spaced axially extending through-bolts 30a. The rings of the ball and socket joints are centered by a shoulder 32 (shown in the encircling ring which is added to the drawing for purposes of designation). An expansion compensation ~pacing 31 is provide~ (shown by the circle to designate the area). The plane of torq~Te support or alignment accommodation is indicated at 33. The possible pivotal motion due to chan~e in alignmen~ of the shafts 21 and 29 is indicated by the arrowea lines ~9aO The driven ball and socket joint includes the outer ring 26 wi~h axially extending pockets and a hub 28 is splined to the shaft 29. Spherical balls 27 seat in the pockets of the ring 26 and in a~ially extending pockets on the hub 28, and the balls are held in place by a cage 21a.
In the arrangement of Figure 4, the coupling illu~trAted allows damping motion of the individual shafts relative to one another in ever~ directionO ~ubs 42 and 55 are mounted on and splined to respective shafts ~1 and 5~.
~ .~
~ub 42 carries a ring 43 and a ring 44 which by axiall~
extending through~bolts provides spacers to mount a drive disk 45 which preferably has a star-like design constituting an inner circular or annular portion with spaced projections. A similar construction is provided in a ring ~4 which mounts on the hub 55. To interconnect the star-like rings 45 and 54, an intermediate element is provided, and pins or bolts 47 and 51 e~tend from the star rings into the elastic rubber spring elements 49 and 53 in the center coupling member 48. Bushings 46 and 52 are provided for the pins 51 and 47. The cou~ling 53 is formed of rubber and is assembled without prestress and admits motion in all directions, but transmits rotary torque. Assimilation and vibrations and stresses is accomoodated, and yet the coupling member 53 remains in its centered position when stationary and when driving in axial alignment with the shaf~s 41 and 56. Cer~ain axial misalignment is accomModated as indicated by the arrowed lines at D~ and axial shifting of the shafts such as due to temperature change is permitted as indicated by the arrowed lines M.
Further, angular cocking of the axis of the shafts is accommodated as indicated by the arrowed dimension A.
Thus, it will be seen tha~ ~e have provided an improved coupling concept which meets the objectives and advantages above set orth and provides particular accommodation in a rail vehicle which are subject to particularly high demands concerning useful life and safety.
~9_ .,,, ~
Claims (5)
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. Double axle drive for rail traction vehicles, comprising a bogie frame mounting a drive motor having a shaft in line with the drive direction of the vehicle, which drive motor drives angular gears, arranged on the wheel axles, via articulated joint couplings having halves which are interconnected in a torsionally elastic fashion whereby a torque support is arranged between the bogie frame and each gear housing in such a fashion that the articulated joint couplings are stressed only as to torsion and bending, characterized in that each articulated joint coupling comprises a ball and socket joint having at least one ball race in each of the two coupling halves, between which there is arranged a centering element for ensuring torsional elasticity and centered on one of the coupling halves, which centering element is in connection radially with the other coupling half via a centering bolt, provided with a sliding sleeve, and which is in connection axially with the other coupling half via a center section having sliding discs.
2. Drive according to claim 1, characterized in that there is arranged, in the centering element for the purpose of trans-ferring the torque, at least one resilient ring.
3. Drive according to claim 2, characterized in that the resilient ring is connected in a bias-free fashion via screw connections with the centering element.
4. Drive according to claim 1, 2 or 3, characterized in that a coup-ling sleeve is designed in two parts, and that, between the two parts, the axially acting sliding discs are arranged.
5. Drive according to claim 1 characterized in that said coupling is formed of three parts with rubber interconnecting-shaped spring elements between the halves, said elements being unstressed in a non-driving relation-ship.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19813149471 DE3149471A1 (en) | 1981-12-14 | 1981-12-14 | DOUBLE AXLE DRIVE FOR RAIL VEHICLES |
| DEP3149471.4 | 1981-12-14 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1200148A true CA1200148A (en) | 1986-02-04 |
Family
ID=6148670
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000415042A Expired CA1200148A (en) | 1981-12-14 | 1982-11-08 | Double axle drive for rail traction vehicles |
Country Status (7)
| Country | Link |
|---|---|
| EP (1) | EP0081640B1 (en) |
| JP (1) | JPS58105870A (en) |
| AT (1) | ATE15168T1 (en) |
| BR (1) | BR8206480A (en) |
| CA (1) | CA1200148A (en) |
| DE (2) | DE3149471A1 (en) |
| ES (1) | ES516074A0 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3702799A1 (en) * | 1987-01-30 | 1988-08-18 | Loehr & Bromkamp Gmbh | Swivel joint for connecting two shaft sections |
| JP2000179465A (en) * | 1998-10-05 | 2000-06-27 | Tominaga Jushi Kogyosho:Kk | Air-cum-water pump for appreciation fish water tank and appreciation fish water tank device with migration passage |
| EP3199418A1 (en) * | 2016-01-26 | 2017-08-02 | Siemens Aktiengesellschaft | Dual axle drive |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR1049411A (en) * | 1950-07-06 | 1953-12-29 | Silentbloc | Elastic coupling device for transmission |
| DE1198615B (en) * | 1957-01-03 | 1965-08-12 | Maschf Augsburg Nuernberg Ag | Elastic coupling |
| DE1206218B (en) * | 1962-01-27 | 1965-12-02 | Demag Ag | Axially and angularly movable coupling |
| JPS4426336Y1 (en) * | 1965-03-17 | 1969-11-05 | ||
| DE1916445A1 (en) * | 1969-02-07 | 1970-09-24 | Barkas Werke Veb | Torsionally flexible cardan shaft |
| JPS521354A (en) * | 1975-06-24 | 1977-01-07 | Kitai Tekkosho:Kk | Shaft coupling device |
| DE2601516A1 (en) * | 1976-01-16 | 1977-07-21 | Thyssen Industrie | DOUBLE AXLE DRIVE FOR RAIL VEHICLES |
-
1981
- 1981-12-14 DE DE19813149471 patent/DE3149471A1/en not_active Withdrawn
-
1982
- 1982-09-29 ES ES516074A patent/ES516074A0/en active Granted
- 1982-10-04 AT AT82109142T patent/ATE15168T1/en not_active IP Right Cessation
- 1982-10-04 DE DE8282109142T patent/DE3265865D1/en not_active Expired
- 1982-10-04 EP EP82109142A patent/EP0081640B1/en not_active Expired
- 1982-11-08 CA CA000415042A patent/CA1200148A/en not_active Expired
- 1982-11-09 BR BR8206480A patent/BR8206480A/en unknown
- 1982-12-07 JP JP57213438A patent/JPS58105870A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| JPS58105870A (en) | 1983-06-23 |
| DE3149471A1 (en) | 1983-06-23 |
| ATE15168T1 (en) | 1985-09-15 |
| ES8306347A1 (en) | 1983-06-01 |
| EP0081640B1 (en) | 1985-08-28 |
| ES516074A0 (en) | 1983-06-01 |
| BR8206480A (en) | 1983-09-27 |
| EP0081640A1 (en) | 1983-06-22 |
| DE3265865D1 (en) | 1985-10-03 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |